|Publication number||US4615383 A|
|Application number||US 06/728,866|
|Publication date||Oct 7, 1986|
|Filing date||Apr 30, 1985|
|Priority date||May 1, 1984|
|Publication number||06728866, 728866, US 4615383 A, US 4615383A, US-A-4615383, US4615383 A, US4615383A|
|Original Assignee||Sanden Corporation|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (14), Referenced by (29), Classifications (13), Legal Events (6)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates to a heat exchanging apparatus, and more particularly to a refrigerant evaporator or condenser for use in, for example, an automobile air conditioner.
Heat exchanging apparatus, such as the serpentine type heat exchanger, is well known as suitable for use in automobile air conditioners as the evaporator or condenser. A prior art serpentine type heat exchanger is illustrated on FIGS. 1 and 2 which show the evaporator.
The evaporator comprises a flat tube 1 which has a multichannel internal construction formed with a number of parallel channels (not shown) and is bent into the form of a serpentine tortuous cross section. One end of flat tube 1 is brazed to an inlet pipe 2 which comunicates which a decompression or expansion means (not shown) in a refrigerating circuit. Therefore, refrigerant flows from inlet pipe 2 into the channels of flat tube 1 and flows from the outlet of outlet pipe 3 into the compressor. A corrugated fin unit 4 is disposed between each of the adjacent or opposed upright portions of flat tube 1, the unit being securely joined to such portions by brazing along their horizontal lines of contact. A protective plate 5 is securely joined by being brazed to each of the corrugated fin units 4 which are joined to the outermost upright portions of flat tube 1, respectively.
In an evaporator with the above-described construction, flat tube 1 as shown on FIG. 2 has the upright portions facing one another connected by an arcuately curved section 1b. For this reason, the corrugated fin unit cannot be disposed within the arcuately curved section 1b. Thus almost all of the air passing through the space within this arcuately curved section 1b moves through without heat exchange with the refrigerant. The efficiency of heat exchange is therefore undesirably reduced.
One solution for solving the above problem is to cover the arcuately curved sections 1b with an air shield plate 6 (FIG. 2) which is integrally formed with a cooling case to prevent the air-flow from passing through the space within arcuately curved sections 1b. However, the air space which is covered by shield plate 6 becomes unavailable space for heat exchange. Therefore, the space efficiency of the heat exchanger, i.e., the ratio of the area which is usefully heat exchanged with air to the volume of the heat exchanger, is reduced.
It is a primary object of the invention to provide an improved heat exchanger which achieves a high efficiency of heat exchange.
It is another object of this invention to provide a heat exchanger wherein the space efficiency is improved, accomplishing this with a compact size while the same heat exchanger volume as prior exchangers is maintained.
The heat exchanger in accordance with the present invention comprises a flat tube which is provided with a plurality of passages therein and bent to form a serpentine tortuous cross section. The heat exchanger with serpentine tortuous cross section has a plurality of parallel portions spaced apart from each other to form horizontal passages for air and connecting portions connected with adjacent ends of these parallel portions. A plurality of corrugated fin units, each of which is folded into a wavy form, are interposed within the horizontal passages, respectively.
Each connecting portion of the flat tube consists of a plurality of arc shaped curved segments connected respectively to adjacent ends of parallel portions of the flat tube, and a center connecting segment connected to the arc shaped curved segments, this connecting segment being curved inwardly to contact against the fin unit in the horizontal passage between adjacent parallel portions.
FIG. 1 is a perspective view of a prior art serpentine type evaporator to illustrate its basic construction.
FIG. 2 is an enlarged front view of a portion of the evaporator of FIG. 1 which is provided with an air cooling shield plate.
FIG. 3 is a perspective view of a serpentine type evaporator in accordance with the present invention.
FIG. 4 is a partial cut-away perspective view of a serpentine type evaporator as shown in FIG. 3.
FIG. 5 is an enlarged front view of a portion of an evaporator as shown in FIG. 3 which is provided with a cooling case.
FIG. 6 is an enlarged front view similar to the portion shown in FIG. 5 illustrating a further arrangement for the cooling case.
Referring to FIGS. 3 and 4, a serpentine type heat exchanging apparatus in accordance with the present invention is shown in the form of a refrigerant evaporator 10. Refrigerant evaporator 10 comprises a flat tube 11 which is made of aluminum and bent into a serpentine tortuous cross section of a longitudinal direction thereof. Corrugated fin units 12, each of which is made of aluminum and folded into wavy form, are disposed between the opposed parallel portions of the flat tube 11.
When flat tube 11 is bent to form the serpentine tortuous cross section, flat tube 11 consists of a plurality of parallel portions 111 spaced apart from each other in the longitudinal direction of the tube, forming a gap between adjacent parallel portions 111, and a plurality of connecting portions 112, each portion 112 connecting with two of the adjacent parallel portions. Connecting portions 112 ensure the capability for flow of refrigerant alternately in opposite directions. When flat tube 11 is positioned to have its parallel portions 111 extending in a vertical direction as shown in FIG. 3, the connecting portions 112 consist of upwardly curved upper portions and downwardly curved lower portions.
As shown in FIG. 4, flat tube 11 is divided into a plurality of refrigerant passageways 11a in order to improve the heat transfer rate. Referring to FIG. 3, one end of the flat tube 11 is brazed to an inlet pipe 13 which communicates with an expansion valve (not shown) in a refrigerant circuit. An outlet pipe 14 which communicates with the suction portion of a refrigerant compressor (not shown) in the refrigerant circuit is brazed on the other end of the flat tube 11.
In the evaporator 10 with the above described construction, each connecting portion 112 comprises a pluality of arc shaped curvatures, as shown in FIGS. 3 and 5. That is, connecting portion 112 comprises two inwardly facing arc shaped segments 112a and 112b, each of which has one end connected with one end of a parallel portion 111 of flat tube 11 and an outwardly facing arc shaped segment 112c which is connected between the two inwardly facing arc shaped segments 112a and 112b. Therefore, connecting portion 112 is formed with a generally M-shaped cross section.
If evaporator 10 is placed in a cooling case 20, connecting portions 112 are covered by a shield plate 21 which is formed integral with cooling case 20, as shown in FIG. 5. In this arrangement, since the vertical height of connecting portion 112 (this height being indicated by L in FIG. 5) can be designed shorter than prior evaporator structures, the shielded space of the evaporator where flow of heat exchanging air is prevented, is reduced. Therefore, the space factor of the evaporator is improved, i.e., open space of the evaporator which is perpendicular to the air flow direction can be reduced while still maintaining the same space heat exchanging area.
Furthermore, if the outer portions of connecting portions 112 are covered by indentations 201a which are integrally formed with lower shield plate 201 and upper shield plate of cooling cover 20, (only lower plate 201 being shown in FIG. 6), heat exchange air passage spaces B1, B2 and B3 is not so large an area. Therefore, the air passed through these spaces is sufficiently heat exchanged with the refrigerant through the connecting portions 112 of flat tube 11.
As mentioned above, the connecting portion of the serpentine type heat exchanger is formed with a generally M-shaped cross section. Therefore, the vertical height of connecting portions 112 in which the corrugated fin units are disposed can be reduced. Thus the extent of open space in evaporator 10 which does not contribute to heat exchange is reduced without influencing the extent of heat exchanging area.
This invention has been described in detail in connection with the preferred embodiments, but these are examples only and this invention is not restricted thereto. It will be easily understood by those skilled in the art that other variations and modifications can be made within the scope of this invention.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US1799626 *||Jul 8, 1929||Apr 7, 1931||Refinery Engineers Inc||Heat exchanger|
|US2322145 *||Nov 2, 1940||Jun 15, 1943||Richard W Kritzer||Heat exchange coil|
|US2792201 *||Aug 19, 1954||May 14, 1957||Gen Motors Corp||Heat exchanger|
|US2886296 *||Feb 14, 1957||May 12, 1959||Gen Motors Corp||Refrigerating apparatus|
|US3042380 *||Apr 20, 1959||Jul 3, 1962||Karmazin John||Heat exchanger construction|
|US3196939 *||Dec 14, 1959||Jul 27, 1965||Hallicrafters Co||Heat exchanger, reservoir, fan and pump assembly|
|US4386652 *||Sep 8, 1980||Jun 7, 1983||North York Mobile Wash Limited||Heat exchange assembly|
|BE513573A *||Title not available|
|DE1239331B *||Jun 27, 1962||Apr 27, 1967||Shell Int Research||Einrichtung zum Verteilen eines Waerme aufnehmenden Mediums, das ueber ein Rohr zugefuehrt wird, auf mehrere Rohre|
|DE2506559A1 *||Feb 17, 1975||Aug 21, 1975||Autobrzdy N P||Waermetauscher|
|DK66267A *||Title not available|
|FR1209680A *||Title not available|
|IT614741A *||Title not available|
|JPS57105690A *||Title not available|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US4829780 *||Jan 28, 1988||May 16, 1989||Modine Manufacturing Company||Evaporator with improved condensate collection|
|US5101890 *||Apr 24, 1990||Apr 7, 1992||Sanden Corporation||Heat exchanger|
|US5197539 *||Feb 11, 1991||Mar 30, 1993||Modine Manufacturing Company||Heat exchanger with reduced core depth|
|US5682944 *||Jun 23, 1995||Nov 4, 1997||Nippondenso Co., Ltd.||Refrigerant condenser|
|US5730212 *||Dec 30, 1996||Mar 24, 1998||Nippondenso Co., Ltd.||Refrigerant condenser|
|US6125922 *||Jun 13, 1997||Oct 3, 2000||Nippondenso Co., Ltd.||Refrigerant condenser|
|US6408941||Jun 29, 2001||Jun 25, 2002||Thermal Corp.||Folded fin plate heat-exchanger|
|US7017655||Dec 18, 2003||Mar 28, 2006||Modine Manufacturing Co.||Forced fluid heat sink|
|US7069980||Oct 14, 2003||Jul 4, 2006||Modine Manufacturing Company||Serpentine, multiple paths heat exchanger|
|US8122729||Mar 12, 2008||Feb 28, 2012||Dri-Eaz Products, Inc.||Dehumidification systems and methods for extracting moisture from water damaged structures|
|US8146651 *||Oct 3, 2008||Apr 3, 2012||Honda Motor Co., Ltd.||Heat exchanger with recessed fins|
|US8290742||Nov 17, 2008||Oct 16, 2012||Dri-Eaz Products, Inc.||Methods and systems for determining dehumidifier performance|
|US8572994||Apr 26, 2010||Nov 5, 2013||Dri-Eaz Products, Inc.||Systems and methods for operating and monitoring dehumidifiers|
|US8784529||Oct 15, 2012||Jul 22, 2014||Dri-Eaz Products, Inc.||Dehumidifiers having improved heat exchange blocks and associated methods of use and manufacture|
|US9089814||Oct 3, 2013||Jul 28, 2015||Dri-Eaz Products, Inc.||Systems and methods for operating and monitoring dehumidifiers|
|US9664450 *||Apr 11, 2014||May 30, 2017||Dana Canada Corporation||Fin support structures for charge air coolers|
|US20040134226 *||Dec 18, 2003||Jul 15, 2004||Kraay Michael L.||Condenser for air cooled chillers|
|US20040194934 *||Oct 14, 2003||Oct 7, 2004||Karl Hofbauer||Serpentine, multiple paths heat exchanger|
|US20070261837 *||Nov 30, 2006||Nov 15, 2007||Modine Manufacturing Company||Compact high temperature heat exchanger, such as a recuperator|
|US20110113824 *||Jul 7, 2009||May 19, 2011||Husnu Kerpicci||Evaporator|
|US20110168367 *||Oct 3, 2008||Jul 14, 2011||Honda Motor Co., Ltd.||Heat Exchanger With Recessed Fins|
|US20140174121 *||Dec 20, 2013||Jun 26, 2014||Keihin Thermal Technology Corporation||Evaporator with cool storage function|
|US20140318751 *||Apr 11, 2014||Oct 30, 2014||Dana Canada Corporation||Fin Support Structures for Charge Air Coolers|
|USD634414||Apr 27, 2010||Mar 15, 2011||Dri-Eaz Products, Inc.||Dehumidifier housing|
|USD731632||Dec 4, 2012||Jun 9, 2015||Dri-Eaz Products, Inc.||Compact dehumidifier|
|USRE37040 *||Apr 2, 1991||Feb 6, 2001||Modine Manufacturing Company||Evaporator with improved condensate collection|
|DE10248665A1 *||Oct 18, 2002||Apr 29, 2004||Modine Manufacturing Co., Racine||Wärmeübertrager in Serpentinenbauweise|
|EP0259198A1 *||Jul 10, 1987||Mar 9, 1988||Valeo Thermique Moteur||Heat-exchanger with U-shaped tubes, more particularly for motor vehicles|
|EP3203176A3 *||Jan 10, 2017||Sep 13, 2017||Hussmann Corporation||Heat exchanger including coil end close-off cover|
|U.S. Classification||165/150, 165/152, 165/172|
|International Classification||F28D1/047, F28F1/02, F28F9/00, F25B39/02|
|Cooperative Classification||F28F9/001, F25B39/02, F28D1/0478|
|European Classification||F25B39/02, F28D1/047F2, F28F9/00A|
|Jun 25, 1985||AS||Assignment|
Owner name: SANDEN CORPORATION 20 KOTOBUKI-CHO, ISESAKI-SHI, G
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:AOKI, HISAO;REEL/FRAME:004423/0461
Effective date: 19850613
|Jul 28, 1987||CC||Certificate of correction|
|Mar 22, 1990||FPAY||Fee payment|
Year of fee payment: 4
|May 17, 1994||REMI||Maintenance fee reminder mailed|
|Oct 9, 1994||LAPS||Lapse for failure to pay maintenance fees|
|Dec 20, 1994||FP||Expired due to failure to pay maintenance fee|
Effective date: 19941012